JP6066708B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll type compressor, and more particularly to a scroll type compressor that suppresses vibration caused by the movement of an Oldham ring that prevents a rotating scroll from rotating.

  A scroll-type compressor used for an air conditioner or a refrigeration apparatus includes a fixed scroll and a orbiting scroll each having a spiral scroll wall. Then, the orbiting scroll is revolved without rotating with respect to the fixed scroll, and the volume of the compression chamber formed between both scroll walls is reduced, thereby compressing the refrigerant in the compression chamber.

In order to prevent the rotation of the orbiting scroll, an Oldham ring is interposed between the orbiting scroll and the housing that supports the orbiting scroll. As is well known, the Oldham ring reciprocates linearly, and therefore becomes a source of excitation force that vibrates the entire compressor in this direction. When the rotation speed of the compressor is low, this excitation force can be allowed, but vibration and noise become remarkable when the rotation speed is high.
Even if other rotating system parts that rotate are unbalanced, it is possible to theoretically eliminate vibration due to unbalance by adding a balance weight to the motor that is the driving source. However, the excitation force due to the Oldham ring cannot be offset by a conventional balance weight (or counterweight) provided for the rotating system parts. This is because the Oldham ring reciprocates linearly, whereas the conventional ballaus weight rotates in accordance with the rotation of the rotation shaft, and the movement directions of the two are different.

  In contrast, Patent Document 1 provides a pair of ring members (a ring member disposed on the outside and a ring member disposed on the inside), and the resultant force of the individual ring members that reciprocate linearly is that of the orbiting scroll. An Oldham coupling is proposed in which the ring members have the same mass and are arranged on the same plane so that the centrifugal force is the same as the centrifugal force generated by the revolution. According to the Oldham coupling of Patent Document 1, the vibrations caused by the movement of the pair of ring members can be reduced by the conventional balance weight and counterweight, so that the noise of the entire device can be reduced and the equipment inside the device can be reduced. It is said that it is possible to avoid adverse effects on

JP-A-8-159050

However, in the Oldham joint of Patent Document 1, the inner ring member (hereinafter, sometimes referred to as a new balance weight) forms a guide groove on the lower surface of the orbiting scroll, and the new balance weight is provided along the guide groove. To reciprocate linearly. Therefore, the operation of the new balance weight follows the movement of the orbiting scroll and cannot be moved in the opposite direction to the orbiting scroll. Therefore, according to the proposal of Patent Document 1, the resultant force of the outer ring member and the inner ring member (new balance weight) is applied in the same direction as the direction in which the centrifugal force of the orbiting scroll works. Since the surface load increases by the resultant force, it can become a new source of vibration and noise, and anxiety arises in terms of the strength of the orbiting scroll itself or the fixed scroll.
The present invention has been made based on such a technical problem, and includes an Oldham coupling that can move a new balance weight used together with an Oldham ring in any direction independently of the movement of the orbiting scroll. An object is to provide a scroll compressor.

In the present invention, the new balance weight is moved by using an eccentric cam provided on the eccentric bush of the main shaft that drives the orbiting scroll. In this case, since the angle at which the eccentric cam is provided can be set arbitrarily, a new balance weight (second balance weight) can be moved in any direction independently of the movement of the orbiting scroll.
That is, the scroll type compressor of the present invention is provided with an eccentric bush, and is rotated by a drive source, a turning scroll that is rotatably connected to the eccentric bushing of the spindle, and the turning scroll facing the turning scroll. A fixed scroll that forms a compression chamber for compression and has a port on the end plate for discharging the compressed refrigerant toward the high-pressure chamber.
The scroll compressor of the present invention regulates the movement of the orbiting scroll so that the orbiting scroll revolves without rotating with respect to the fixed scroll, and the orbital movement that reciprocates linearly in the first direction and the eccentric bush and the orbiting movement. a first balance weight for an eccentric cam for pivoting movement with eccentric bushing, the rotation of the main shaft, and a second balance weight for linear reciprocating motion in the second direction via the eccentric cam, the second balance weight characterized that you linear reciprocating motion in the second direction forming an arbitrary angle other than the first direction parallel to the direction of linear reciprocating motion of the Oldham ring.
The second balance weight preferably reciprocates linearly in a second direction orthogonal to the first direction of the linear reciprocation of the Oldham ring.

In the scroll compressor of the present invention, the first balance weight is made to function as an eccentric cam, and the second balance weight is arranged in the same plane inside the Oldham ring, and the first direction of the linear reciprocating motion of the Oldham ring is It is preferable to make the 2nd direction of the linear reciprocation of a 2nd balance weight orthogonal.
According to this scroll type compressor, it is not necessary to prepare an eccentric cam separately. Further, since the second balance weight is arranged in the same plane inside the Oldham ring, it is not necessary to consider the balance of the mass in the axial direction.

The present invention is not limited to a mode in which the first balance weight functions as an eccentric cam, and an eccentric cam can be provided separately from the first balance weight. This eccentric cam can be provided at a position of a rotation angle different from that of the first balance weight. This suggests that an eccentric cam can be provided at an arbitrary rotation angle. Also in this form, it is preferable that the second balance weight is disposed inside the Oldham ring.
The second balance weight includes a main body and a cam groove provided in the center of the main body. The second balance weight is provided inside the Oldham ring, and the eccentric cam acts from the inside of the cam groove. It is preferable to perform linear reciprocation.
In addition, the second balance weight preferably has a component of linear reciprocation in the first direction of the linear reciprocation of the Oldham ring.

According to the present invention, the second balance weight 50 is moved via the eccentric cam provided on the eccentric bush to rotate the main shaft. The eccentric cam can be attached to the eccentric bush at an arbitrary angle. Therefore, according to this embodiment, the direction in which the second balance weight reciprocates linearly can be arbitrarily set. For example, according to the present invention, the second balance weight can be moved in the direction opposite to the direction in which the centrifugal force of the orbiting scroll is generated.

It is a longitudinal section of a scroll type compressor concerning this embodiment. The Oldham ring used for the scroll compressor of Drawing 1 is shown, (a) is a top view and (b) is a IIb-IIb line arrow sectional view of (a). The 2nd balance weight used for the scroll type compressor of Drawing 1 is shown, (a) is a top view, (b) is a IIIb-IIIb arrow sectional view of (a), and (c) is IIIc of (a). FIG. It is a figure which shows operation | movement of the 2nd balance weight 50 for every rotation angle of 45 degree | times, (a) is 0 degree | times, (b) is 45 degree | times, (c) is 90 degree | times, (d) is an operation state of 135 degree | times. Show. Continuing to FIG. 4, (a) is 180 degrees, (b) is 225 degrees, (c) is 270 degrees, and (d) is 315 degrees. FIG. 5 is a diagram showing the Oldham ring 40 added to FIG. 4, wherein (a) shows an operating state of 0 degrees, (b) shows 45 degrees, (c) shows 90 degrees, and (d) shows an operating state of 135 degrees. Continuing to FIG. 6, (a) is 180 degrees, (b) is 225 degrees, (c) is 270 degrees, and (d) is 315 degrees. The modification of this embodiment is shown, (a) is a top view, (b) is a VIIIb-VIIIb arrow directional cross-sectional view of (a).

Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
As shown in FIG. 1, the vertical scroll compressor 10 includes a main shaft 12, a turning scroll 20 that rotates together with the main shaft 12, and a fixed scroll 30 that is fixed to the housing 11. .
A scroll compressor (hereinafter simply referred to as “compressor”) 10 is a compression chamber formed between a revolving scroll 20 and a fixed scroll 30 by introducing a refrigerant into the housing 11 from a refrigerant introduction port P1 formed in the housing 11. The refrigerant is compressed. The compressed refrigerant is discharged from a refrigerant discharge port P <b> 2 formed in the housing 11.

In the orbiting scroll 20, a wrap wall 22 having a predetermined height is formed integrally with a disc-shaped end plate 21. The orbiting scroll 20 is supported by the bearing 14 of the housing 11 via an Oldham ring 40 described later.
On the other hand, in the fixed scroll 30, a spiral wrap wall 32 is formed on the end plate 31 that faces the orbiting scroll 20 and meshes with the wrap wall 22 of the orbiting scroll 20.

In this way, the orbiting scroll 20 and the fixed scroll 30 combine the wrap wall 22 and the wrap wall 32 with each other. Thereby, a compression chamber PR is formed between the orbiting scroll 20 and the fixed scroll 30.
As a result, the refrigerant introduced into the compression chamber PR from the outer peripheral side of the orbiting scroll 20 and the fixed scroll 30 is sequentially sent from the outer peripheral side to the inner peripheral side as the orbiting scroll 20 revolves relative to the fixed scroll 30. And compressed. The refrigerant compressed in the compression chamber PR is a discharge hole 37 formed in the fixed scroll 30, a reed valve 38 provided in the discharge hole 37, and a lead provided in an upper cover 39 provided so as to cover the fixed scroll 30. The refrigerant is discharged from the refrigerant discharge port P2 formed on the other end side of the housing 11 through the valve 38.

  Both ends of the main shaft 12 are rotatably supported by the housing 11 via bearings 13 and 14. The main shaft 12 is rotationally driven by a motor 17 including a stator 15 fixed to the inner surface of the housing 11 and a rotor 16 fixed to the outer peripheral surface of the main shaft 12 and facing the stator 15. The main shaft 12 is configured to be rotationally driven by one end of the main shaft 12 projecting outside through the housing 11 and connected to one end of the main shaft 12 by a driving source (not shown) such as an engine or a motor provided outside. It can also be.

  An eccentric bush 18 protrudes from the other end of the main shaft 12 at a position eccentric from the central axis of the main shaft 12 by a predetermined dimension. A recess 23 for accommodating the eccentric bush 18 is formed on the main shaft 12 side of the orbiting scroll 20. The eccentric bush 18 is inserted into the recess 23 via a drive bush (bearing) 24, whereby the orbiting scroll 20 is rotatably held by the eccentric bush 18. Thereby, the orbiting scroll 20 is provided eccentrically by a predetermined dimension with respect to the center of the main shaft 12, and when the main shaft 12 rotates around its axis, the orbiting scroll 20 is eccentric with respect to the center of the main shaft 12. Performs rotation (revolution) with the dimensions as the radius. An Oldham ring 40 is interposed between the orbiting scroll 20 and the main shaft 12 so that the orbiting scroll 20 does not rotate while revolving.

As shown in FIG. 2, the Oldham ring 40 has an annular main body 41, a pair of upper claws 43 provided at positions facing each other across the center of the main body 41 on the upper surface of the main body 41, and the upper claws 43. And a pair of lower claws 45 provided on the lower surface at a position shifted by 90 ° in the circumferential direction of the main body 41. The upper side here means the side facing the orbiting scroll 20. The same applies to the following. A pair of guide grooves (not shown) for slidably fitting the upper claws 43 are formed on the lower surface of the orbiting scroll 20, and the lower claws 45 are connected to the upper claws 43 on the upper surface of the support housing. A pair of guide grooves (not shown) are slidably fitted in a direction perpendicular to the sliding direction.
Then, the upper claw 43 and the lower claw 45 are respectively fitted in the above-described guide grooves, the Oldham ring 40 reciprocates linearly with respect to the bearing 14, and the orbiting scroll 20 moves with respect to the Oldham ring 40 as described above. The orbiting scroll 20 revolves relative to the bearing 14 by reciprocating linearly in a direction perpendicular to the reciprocating direction.

The main shaft 12 includes a first balance weight 25.
The first balance weight 25 is for balancing the dynamic unbalance due to the orbiting orbiting motion of the orbiting scroll 20. The first balance weight 25 is symmetrical to the eccentric bush 18 on the main shaft 12, that is, in phase with the orbiting orbiting motion of the orbiting scroll 20. Are arranged and fixed so as to be rotated by 180 degrees.
The first balance weight 25 is fixed to the eccentric bush 18 of the main shaft 12 and, as shown in FIG. 4, a connection piece 25a having a substantially fan shape in plan view, and standing upward from the connection piece 25a. And a main body 25b. As for the main body 25b, the guide surface 25c of the outer periphery has comprised circular arc shape by planar view. The second balance weight 50 can be driven by the guide surface 25c acting on the second balance weight 50 from the inside of the cam groove 53 of the second balance weight 50 described below.
The main shaft 12 is formed with a lubricating oil passage 12 a for supplying the lubricating oil sucked up from the oil reservoir at the bottom of the housing 11 from the upper end of the main shaft 12 to the drive bush 24 between the main shaft 12 and the recess 23. Yes.

The main shaft 12 includes a second balance weight 50.
The second balance weight 50 is for balancing dynamic unbalance due to the reciprocating linear motion of the Oldham ring 40, and in a direction orthogonal to the motion direction of the Oldham ring 40 as the first balance weight 25 rotates. Reciprocates linearly. For this purpose, the second balance weight 50 is arranged around the first balance weight 25.

  As shown in FIG. 3, the second balance weight 50 includes a main body 51 having a rectangular shape in plan view, a rounded rectangle cam groove 53 penetrating the front and back at the center of the main body 51, and a main body 51. And a pair of lower claws 55 provided at positions opposed to each other across the center of the main body 51 on the lower surface thereof. The cam groove 53 has a major axis formed along the short direction (or width direction) of the main body 51, and the pair of lower claws 55 are arranged at both ends along the long direction (or length direction) of the main body 51. It is formed in the part. However, since the pair of lower claws 55 are slidably fitted in a pair of guide grooves formed in the bearing 14, the movement direction of the second balance weight 50 is the main body even when a driving force is applied. It is regulated along the longitudinal direction of 51. This guide groove is the same as the guide groove for the Oldham ring 40.

The second balance weight 50 accommodates the first balance weight 25 in the cam groove 53. When the first balance weight 25 rotates with the rotation of the main shaft 12, the guide surface 25 c acts on the second balance weight 50 from the inside of the cam groove 53, whereby the second balance weight 50 can be driven. Since the lower claw 55 is slidably fitted in the guide groove 49, the second balance weight 50 reciprocates linearly along the longitudinal direction of the main body 51.

Now, the operation of the compressor 10 having the above configuration will be described.
When the motor 17 is driven, the main shaft 12 rotates about the axis. Then, the eccentric bush 18 revolves around the axis of the main shaft 12. Along with this, the orbiting scroll 20 to which the eccentric bush 18 is linked revolves with respect to the fixed scroll 30 because the Oldham ring 40 prevents rotation. Thereby, each contact location of the wrap walls 22 and 32 of each scroll 20 and 30 moves toward the center part of a scroll mechanism, and the compression chamber PR moves spirally toward this center part in connection with this. While shrinking. Through these series of operations, the low-pressure refrigerant gas flows into the compression chamber PR from the refrigerant introduction port P1. The refrigerant flowing into the compression chamber PR is compressed to a high pressure, reaches the center of the compression chamber PR, passes through the discharge hole 37, and is discharged from the refrigerant discharge port P2.

  Further, during this compression operation, the lubricating oil pumped up by an oil supply pump (not shown) is supplied to the radial bearing on the outer peripheral side of the main shaft 12 and the thrust bearing at the upper end portion of the main shaft 12 through the lubricating oil passage 12a. The sliding portion of the main shaft 12 and the orbiting scroll 20 is lubricated.

Next, the operation in this embodiment will be described.
The Oldham ring 40 interposed between the orbiting scroll 20 and the bearing 14 slides in the left and right direction (first direction) in FIG. An exciting force that vibrates the compressor 10 in the sliding direction is generated.
On the other hand, the second balance weight 50 disposed inside the Oldham ring 40 slides in a direction perpendicular to the paper surface of FIG. 1 and generates an excitation force that vibrates the compressor 10 in this sliding direction. An example of the operation of the second balance weight 50 is shown in FIGS.

  As shown in FIGS. 4 and 5, when the eccentric bush 18 pivots according to the rotation of the main shaft 12, the first balance weight 25 pivots about the central axis of the eccentric bush 18 as a rotation axis. As a result, the first balance weight 25 acts on the second balance weight 50 from the inside of the cam groove 53 to cause the second balance weight 50 to turn. That is, the second balance weight 50 apparently performs a reciprocating motion in the vertical and horizontal directions in the figure about the rotation axis of the main shaft 12. However, as described above, the second balance weight 50 is fitted into the pair of guide grooves in which the pair of lower claws 55 are formed in the bearing 14. Therefore, the movement of the second balance weight 50 relative to the bearing 14 is restricted in the direction in which the guide groove is formed (the longitudinal direction of the main body 51 of the second balance weight 50). 4 and 5 refers to the rotation angle of the eccentric bush 18, and the definition of the rotation angle of 0 ° will be described later.

Next, the Oldham ring 40 is added to the second balance weight 50, and the operation of both will be described with reference to FIGS. In the following description, the rotation angle of the eccentric bush 18 is 0 ° when the second balance weight 50 is closest to the left side and the Oldham ring 40 is closest to the right side. When the rotation angle is 0 °, the center of the second balance weight 50 and the Oldham ring 40 in the vertical direction in the figure coincide. In the description of FIG. 6 and FIG.
As the eccentric bush 18 rotates clockwise, the second balance weight 50 is displaced upward and to the right. When the rotation angle reaches 90 °, the second balance weight 50 approaches the uppermost side. About the left-right direction, it is located at the center of the displacement stroke. The Oldham ring 40 is located at the center of the displacement stroke in the left-right direction.
When the eccentric bush 18 further rotates, the second balance weight 50 starts to be displaced downward and is displaced to the right. When the rotation angle reaches 180 °, the second balance weight 50 is positioned at the center of the displacement stroke. The Oldham ring 40 is located on the leftmost side.
When the eccentric bush 18 further rotates, the second balance weight 50 continues to be displaced downward and to the right. When the rotation angle reaches 270 °, the second balance weight 50 is positioned at the lowest position in the vertical direction. The Oldham ring 40 is located at the center of the displacement stroke in the left-right direction.
When the eccentric bush 18 further rotates, the rotation angle returns to the state of 0 ° ((a) in FIG. 6).

As described above, the Oldham ring 40 and the second balance weight 50 arranged on the inner side of the Oldham ring 40 reciprocate linearly in directions orthogonal to each other (the X direction and the Y direction, respectively). In addition, the Oldham ring 40 and the second balance weight 50 can be regarded as being arranged on the same plane, and have the same mass. Therefore, the X-direction and Y-direction exciting forces (referred to as F ₄₀ and F ₅₀ ) by the Oldham ring 40 and the second balance weight 50 are equal, and the resultant force acts on the entire apparatus. The two exciting forces increase or decrease according to the amount of displacement of the orbiting scroll 20 in the X direction and the amount of displacement in the Y direction, respectively. The exciting forces F ₄₀ and F ₅₀ are the Oldham ring 40 and the second balance weight. It changes sinusoidally with 50 slide movements (each movement in the X and Y directions). For this reason, the resultant force of the excitation forces F ₄₀ and F ₅₀ acts as a constant centrifugal force.

Here, the exciting forces F40 and F50 by the Oldham ring 40 and the second balance weight 50 are obtained by the equations (1) and (2), respectively, and the resultant force is (F ₄₀ ² · F ₅₀ ² ) ^1/2. It becomes.
Here, since m ₄₀ and m ₅₀ are equal, the resultant force is expressed by Equation (3), and a constant centrifugal force based on this resultant force acts on the compressor 10.
F ₄₀ = m ₄₀ · r · ω ² · sinθ (1)
F ₅₀ = m ₅₀ · r · ω ² · cos θ (2)
m ・ r ・ ω ² (3)
m ₄₀ : mass of Oldham ring 40 m ₅₀ : mass of second balance weight 50 r: revolution radius of orbiting scroll 20 ω: angular velocity of orbiting scroll 20 θ: rotation angle of orbiting scroll 20

  Thus, the compressor 10 swirls the force generated as the Oldham ring 40 and the second balance weight 50 move by providing the Oldham ring 40 and the second balance weight 50 as a pair. It can be handled in the same manner as the centrifugal force generated with the rotation of the scroll 20. Furthermore, the direction of the centrifugal force generated by the resultant force is generated in the same direction as the centrifugal force generated by the revolution of the orbiting scroll 20.

  For this reason, the centrifugal force due to the movement of the Oldham ring 40 and the second balance weight 50 can be offset by appropriately setting the mass of the first balance weight 25. Typically, the mass of the first balance weight 25 may be set slightly larger than when the second balance weight 50 is not provided.

As described above, according to the compressor 10, the second balance weight 50 is provided in addition to the Oldham ring 40 and the first balance weight, and the resultant force of the Oldham ring 40 and the second balance weight 50 that reciprocates linearly is swiveled. The centrifugal force is the same as the centrifugal force generated by the revolution of the scroll 20.
By doing so, the compressor 10 can reduce the vibration accompanying the operation of the Oldham ring 40.

  In the above, the first balance weight 25 has a role as an eccentric cam for driving the second balance weight 50. For example, as shown in FIG. It can also be provided on the eccentric bush 18. The eccentric cam 60 has the same shape as the first balance weight 25, but the attachment angle with respect to the eccentric bush 18 is different from that of the first balance weight 25. That is, the first balance weight 25 is provided in an opposite direction by 180 degrees to the eccentric direction of the orbiting scroll 20, but the eccentric cam 60 can be attached to the eccentric bush 18 at an arbitrary angle with respect to the orbiting scroll 20. it can.

  As described above, the rotation of the main shaft 12 moves the second balance weight 50 via the eccentric cams (first balance weight 25, eccentric cam 60) provided on the eccentric bush 18. The eccentric cam can be attached to the eccentric bush 18 at an arbitrary angle. Therefore, according to this embodiment, the direction in which the second balance weight 50 reciprocates linearly can be arbitrarily set. For example, the second balance weight 50 can be moved in a direction opposite to the direction in which the centrifugal force of the orbiting scroll 20 is generated.

  Moreover, according to this embodiment, the reciprocating movement distance (stroke amount) of the second balance weight 50 can be arbitrarily set. That is, according to the present embodiment, the stroke amount can be arbitrarily set by changing the eccentric amount of the eccentric cam (the first balance weight 25, the eccentric cam 60). This suggests that the mass of the second balance weight 50 can be arbitrarily set. In the present embodiment, in order for the inertial force of the second balance weight 50 to be equivalent to the inertial force of the Oldham ring 40, either the eccentric amount or the mass may be adjusted. For example, the necessary inertia force can be obtained by reducing the mass of the second balance weight 50 while increasing the amount of eccentricity or increasing the mass of the second balance weight 50 while reducing the amount of eccentricity.

Furthermore, in this embodiment, since the second balance weight 50 is fitted to the eccentric cam 50 and the lower claw 55 only needs to be fitted to the guide groove of the bearing 14, the assemblability is good.

In the above embodiment, the scroll type compressor in which the motor 17 that is the drive source of the compression mechanism is assembled inside the housing 11 is taken as an example. However, in the present invention, the drive source of the compression mechanism is the outside of the housing 11. The present invention can be applied to a scroll compressor provided in the above.
In addition to this, as long as it does not depart from the gist of the present invention, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate.

DESCRIPTION OF SYMBOLS 10 Scroll type compressor 11 Housing 12 Main shaft 13 Bearing 15 Stator 16 Rotor 20 Orbiting scroll 21 End plate 25 First balance weight 25a Connection piece 25b Main body 25c Guide surface 30 Fixed scroll 31 End plate 38 Reed valve 39 Upper cover 40 Oldham Ring 41 Main body 50 Second balance weight 51 Main body P1 Refrigerant introduction port P2 Refrigerant discharge port

Claims (6)

A spindle provided with an eccentric bush and driven to rotate by a drive source;
An orbiting scroll rotatably connected to the eccentric bush of the main shaft;
A fixed scroll that forms a compression chamber that compresses the refrigerant by facing the orbiting scroll, and has a port on the end plate that discharges the compressed refrigerant toward the high-pressure chamber;
An Oldham ring that regulates the movement of the orbiting scroll so that the orbiting scroll revolves without rotating with respect to the fixed scroll, and reciprocates linearly in a first direction ;
A first balance weight that swivels together with the eccentric bush;
An eccentric cam rotating with the eccentric bush;
A second balance weight that linearly reciprocates in the second direction via the eccentric cam by rotational driving of the main shaft;
Equipped with a,
The second balance weight is
Scroll compressor characterized that you linear reciprocating motion to the second direction forming an arbitrary angle other than a direction parallel to the first direction of the linear reciprocating motion of the Oldham ring. The second balance weight is
Reciprocating linearly in the second direction orthogonal to the first direction of linear reciprocation of the Oldham ring ;
The scroll compressor according to claim 1. The first balance weight functions as the eccentric cam;
The second balance weight is disposed inside the Oldham ring;
The second direction is perpendicular to the linear reciprocating motion of the first direction of the linear reciprocating motion of the Oldham ring the second balance weight,
The scroll type compressor according to claim 1 or 2 . The eccentric cam is provided at a position of a rotation angle different from that of the first balance weight;
The second balance weight is disposed inside the Oldham ring;
The scroll compressor according to claim 1. The second balance weight is
A main body, and a cam groove provided in the center of the main body,
Provided inside the Oldham ring,
When the eccentric cam acts from the inside of the cam groove, the second balance weight performs linear reciprocation.
The scroll compressor as described in any one of Claims 1-3. The second balance weight is
In the first direction of the linear reciprocation of the Oldham ring also has a component of linear reciprocation.
The scroll type compressor according to any one of claims 1 to 5.

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